Air heating unit of the air-conditioning

ABSTRACT

The present invention relates to an air heating unit of the air-conditioning including a compressor, a thermal compensation device and an air cooled condenser connected sequentially with one another by pipeline to define a refrigeration cycle. A high-temperature gaseous refrigerant flowing in inner and outer tubes of the thermal compensation device performs transfers heat with an intermediate-temperature liquid refrigerant flowing in mid tube, so that temperature of a liquid refrigerant flowing in a capillary gap between mid and inner tubes is increased to achieve liquid expand and flow restrained effects. The capillary gap can block bubbles of super heat from entering and suppress the liquid refrigerant from flowing through. Thus, a limited amount of liquid refrigerant can be sucked into the compressor at a low pressure without having lubricating oil to be turned cold. This air heating unit eliminates the use of evaporators other than in a conventional refrigeration system.

FIELD OF THE INVENTION

The present invention relates to an air heating unit of theair-conditioning, and more particularly to the air heating unit of theair-conditioning has designed with no evaporator.

BACKGROUND OF THE INVENTION

Conventional air-conditioning equipment generally includes four basicitem of device, respectively: an evaporator, a compressor, a condenserand a thermal expansion valve, and the four major item of device areconnected sequentially with one another by a pipeline to define arefrigeration cycle.

According to the operation principle of the conventionalair-conditioning equipment, a low-pressure low-temperature refrigerantabsorbs heat to produce a refrigeration effect in the evaporator. Inother words, air blows through the evaporator to lower the temperatureof air, and the refrigerant is evaporated to form a low-pressurelow-temperature gaseous refrigerant, and then sucked back to thecompressor through a suction line and discharged to become ahigh-pressure and high-temperature gaseous.

The high-pressure high-temperature gaseous refrigerant is dischargedthrough a discharge line into the condenser for heat exchange to producea heating effect. In other words, air passes through the condenser toincrease the temperature of air, so that the high-pressurehigh-temperature gaseous refrigerant becomes liquid, and thehigh-pressure liquid refrigerant enters a thermal expansion devicethrough a liquid line, and the thermal expansion device controls theflow of the refrigerant and disperses the liquid refrigerant into theevaporator in low pressure, low temperature mist refrigerant to absorbheat to provide a cooling effect in the evaporator and a heating effectin the condenser.

The aforementioned air-conditioning equipment has a different nameaccording to different functions, such as an air-conditioner, a heatpump, a refrigerator, and a dehumidifier, etc. For example, thedehumidifier introduces air into the evaporator to dehumidify the airand lower the temperature, and then absorb heat from the condenser, sothat the discharged air has a higher temperature and a lower enthalpythan the intake air, and thus the dehumidifier is considered as anair-conditioning equipment with the dehumidification and heating effect.

In view of the aforementioned air-conditioning equipments, theevaporator is a necessary device to evaporate the refrigerant into alow-pressure low-temperature gaseous refrigerant, a heat pump forexample, in a low-temperature environment, the refrigerant in outdoorevaporator cannot absorb enough heat from the cold temperatureenvironment, but is absorbed from compressor, and the crank case of thecompressor will freeze, so cannot generate compression heat. Since theheat pump cannot function right in severe cold weather, therefore mostof them require electric heating elements to produce an indoor heatingeffect. However, the high temperature of the electric heating elementscauses an oxygen burning phenomenon, and thus requires improvements.

SUMMARY OF THE INVENTION

One primary objective of the present invention is to provide an airheating unit of the air-conditioning that eliminates thedevice-evaporator, so that the operation of the air heating unit is notlimited by cold weathers to provide the indoor heating effect in asevere cold weather.

Another objective of the present invention is to provide an air heatingunit of the air-conditioning, wherein the compression heat generated bythe compressor is discharged through the condenser, the indoor airtemperature is increased, and the indoor moisture is dehumidified, sothat there is no longer any issue of the oxygen burning phenomenon.

To achieve the aforementioned objective, the present invention providesan air heating unit of the air-conditioning, comprising: a compressor,with a discharge end coupled to a first link tube line provided forhigh-pressure high-temperature gaseous refrigerant and oil; a thermalcompensation device, having an inner tube, a mid tube and an outer tubeof different diameters, the mid tube being sheathed with the outer tubetherein, and the inner tube being sheathed with the mid tube therein toform a tri-tubing structure of thermal compensation device, and anoutput end of the first link tube line being coupled to the inner andouter tubes, for facilitating the high-pressure high-temperature gaseousrefrigerant charged into the inner and outer tubes, and an output end ofthe inner and outer tubes being coupled to a second link tube line forflowing the high-pressure high-temperature gaseous refrigerant and oil;an air cooled condenser, including an internal condenser coil installedtherein and having an intake end coupled to an output end of the secondlink tube line, a fan installed outside the air cooled condenser, suchthat the high-pressure high-temperature gaseous refrigerant enteringinto the condenser coil to change state to form a high-pressureintermediate-temperature liquid refrigerant by air blow, and thecondensed liquid refrigerant and oil still containing bubbles of superheat inside output end of the condenser coil enter into a third linktube line, in which a thermostat sensor attached thereon for measuringand detecting the liquid refrigerant reaches a predetermined limitationof temperature to control the fan to be turned on or off, and the fan isoperated in intermittently to blow air to the condenser for heatingonce; and the mid tube, having an intake end linked to the third linktube line and an output end coupled to a fourth link tube linerespectively, such that the intermediate-temperature liquid refrigerantflowing and passing through mid tube performs a heat exchangerespectively with the high-temperature gaseous refrigerant flowing inthe inner tube and the outer tube, and the intermediate-temperature ofliquid refrigerant is expanded by heat gain so do the pressure isincreased, and the bubbles of super heat in the liquid refrigerant areblocked outside the inlet of capillary gap between the mid tube and theinner tube; the liquid refrigerant and oil containing no bubbles ofsuper heat flowing out from the outlet of capillary gap between the midtube and the inner tube flows and enters into the fourth link tube line,the high pressure is depressed at once and the temperature is lowered tobecome unsaturated liquid refrigerant flowing; and an output end of thefourth link tube line being coupled to a liquid-gas separator todisperse the unsaturated liquid refrigerant into it. In order to dropthe pressure and the temperature again inside liquid-gas separator toform low-pressure suitable temperature, the low-pressure suitabletemperature liquid refrigerant and oil are sucked from a suction end ofthe compressor to define a refrigeration cycle.

BRIEF DESCRIPTION OF THE DRAWINGS

The technical characteristics, contents, advantages and effects of thepresent invention will be apparent with the detailed description of apreferred embodiment accompanied with the illustration of relateddrawings as follows.

FIG. 1 is a schematic view illustrating the pipeline layout of an airheating unit of the air-conditioning to the present invention;

FIG. 2 is a schematic view illustrating the refrigerant flowingdirection of an air heating unit of the air-conditioning to the presentinvention; and

FIG. 3 is a cross-sectional view of a thermal compensation device to thepresent invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

With reference to FIG. 1 to FIG. 3 for the air heating unit of theair-conditioning in accordance with the present invention, the airheating unit comprises a compressor 1, a thermal compensation device 2,an air cooled condenser 3, and four link tube lines 4, 5, 6, 7.

The compressor 1 is a prior art, such as an electric motor, e.g. used asa motive power to facilitate a low-pressure low-temperature gaseousrefrigerant such as the 134A refrigerant and a lubricating oil(hereinafter referred to as “oil”) contained in the compressor 1 iscompressed into a high-pressure high-temperature gaseous refrigerant.For example, the gaseous refrigerant and oil at approximately 107Celsius degree moves (in a direction as indicated by the arrows in thefigures) from a discharge end 11 of the compressor 1 into the first linktube line 4. Wherein, an intake end of the first link tube line 4 iscoupled to the discharge end 11 of the compressor 1, and an output endof the first link tube line 4 is coupled to a double-fork shunt tube 24of a thermal compensation device 2.

The thermal compensation device 2 is a tri-tubing structure formed bysheathing an inner tube 21 into a mid tube 22, and the mid tube 22 intoan outer tube 23. Wherein, the inner tube 21, the mid tube 22 and theouter tube 23 are made of metal such as copper or a copper alloy andhave different diameters such as ⅜″, ½″ and ¾″ inches respectively.Intake and output ends of the inner tube 21 and the outer tube 23 arecoupled to a double-fork shunt tube 24 and a manifold tube 25respectively to branch the aforementioned high-pressure high-temperaturegaseous refrigerant and oil by the shunt tube 24 to enter and flow inthe inner tube 21 and the outer tube 23, so that the high-pressurehigh-temperature gaseous refrigerant in the inner tube 21 and the outertube 23 flows respectively through a condenser 3 back to the mid tube 22to compensate heat with the fast-flowing high-pressureintermediate-temperature liquid refrigerant, so as to perform a heattransfer to the liquid refrigerant. As such, the high-temperaturegaseous refrigerant collected by the manifold tube 25 flows towards asecond link tube line 5, and the temperature of the high-temperaturegaseous refrigerant flowing in the second link tube line 5 dropsslightly to approximately 103 Celsius degree.

An intake end of second link tube line 5 is coupled to the manifold tube25, and an output end of the second link tube line 5 is coupled to thebottom inlet of air cooled condenser 3 and the condenser coil 31 are inseries connection to provide the high-temperature gaseous refrigerantand oil to enter. A conventional fan 32 is provided and the condensercoil 31 is surrounded by a plurality of heat dissipation fins (priorart, not shown in the present invention) to achieve the heat dissipateand condensed effects, so that the high-pressure high-temperaturegaseous refrigerant saturated in the condenser coil 31 is cooled tochange its state into liquid with high-pressure intermediate-temperaturecontaining bubbles of super heat, and the condensed liquid refrigerantand oil flow out from the output end of condenser coil 31 at the top ofthe condenser 3 and discharged into a third link tube line 6. Since theliquid refrigerant charged to the condenser coil 31 is full saturatedand satisfied, the heat saturation effect can be achieved effectively.

Wherein, the third link tube line 6 is attached with a thermostat sensor61, such that if the temperature of the liquid refrigerant passingthrough the third link tube line 6 detected by the thermostat sensor 61reaches a predetermined limitation of temperature such as 75 Celsiusdegree, the fan 32 will be turned on immediately to blow air to thecondenser 3 to dissipate the heat of the condenser 3 and turn the airpassing through the condenser 3 into hot air for the indoor heatingpurpose. If the temperature of the liquid refrigerant passing throughthird link tube line 6 detected by the thermostat sensor 61 is lowerthan the predetermined thermostat temperature such as 75 Celsius degree,the fan 32 will be turned off immediately to stop blowing air to thecondenser 3. The control with the predetermined temperature of thethermostat sensor 61 keeps the fan 32 to blow air to the condenser 3intermittently and turn the air passing through the condenser 3 into hotair to achieve an indoor heating effect.

In addition, the gaseous refrigerant enters from the bottom inlet of thecondenser 3 and condensed into liquid refrigerant then flows out fromthe outlet in top of the condenser 3, and such arrangement has thefollowing advantage. The high-temperature gaseous refrigerant isimpacted and mixed with the intermediate-temperature liquid refrigerantin the condenser coil 31, so that the liquid refrigerant receives theheat of the super heat of gaseous refrigerant to expedite theliquefaction of the gaseous refrigerant, and a large quantity ofliquefied refrigerant can be saturated and satisfied in the condensercoil 31 to achieve a heat saturation effect effectively.

An output end of third link tube line 6 is coupled to the mid tube 22 ofthe thermal compensation device 2, such that theintermediate-temperature liquid refrigerant, oil and bubbles of superheat flowing into third link tube line 6 flows towards the mid tube 22.Since the diameters (or sizes) of the mid tube 22 and the inner tube 21is ½″ and ⅜″ inches respectively, therefore the gap in between is verysmall so as to leave a capillary gap and achieve a kind of capillarytube effect. The intermediate-temperature liquid refrigerant flowing inthe mid tube 22 perform heat transfer with the high-temperature gaseousrefrigerant flowing in the inner tube 21 and the outer tube 23, so thatthe liquid refrigerant is expanded by heat gain, and thus bubbles ofsuper heat are blocked outside the inlet capillary gap 26 between themid tube 22 and the inner tube 21 to achieve the flow restrained effectsimilar to an expansion valve or a capillary tube.

The liquid refrigerant and oil are not containing any bubbles of superheat flowing out from the output end of the mid tube 22 enters into afourth link tube line 7. Since the fourth link tube line 7 has adiameter greater than the outlet capillary gap 27 between the mid tube22 and the inner tube 21, therefore when the intermediate-temperatureliquid refrigerant are not containing bubbles of super heat enters andflows into fourth link tube line 7, the pressure is depressed at onceand the temperature is lowered to form a low-pressureintermediate-temperature unsaturated liquid refrigerant flowing, andmeasurements shows that the temperature of the liquid refrigerant offourth link tube line 7 is 68 Celsius degree.

An output end of fourth line tube line 7 is coupled to a conventionalliquid-gas separator 8 accomplished with the compressor 1, and theinternal diameter of the liquid-gas separator 8 is greater than fourthlink tube line 7 for many times. After the unsaturated liquidrefrigerant dispersed into the liquid-gas separator 8, the pressure andtemperature are depressed again to a lower-pressure with suitabletemperature such as a liquid refrigerant at approximately 38 Celsiusdegree. This temperature will not lower as the refrigeration effect likethe lubricating oil passing through the evaporator does, such that thelubricating oil is in a sticky form which is unfavorable for thelubrication of the compressor. After the low-pressure suitabletemperature liquid refrigerant and oil dispersed into the liquid-gasseparator 8 is sucked by the suction power of the suction end 12 of thecompressor 1 and compressed to high-pressure high-temperature gaseousrefrigerant discharged by discharge end 11 into first link tube line 4to define a refrigeration cycle.

In summation of the description above, the present invention has thefollowing advantages. The high-temperature gaseous refrigerant flowingin the inner and outer tubes of the thermal compensation devicetransfers heat with the intermediate-temperature liquid refrigerantflowing in the mid tube, so that the liquid refrigerant flowing into theinlet of capillary gap between the mid tube and the inner tube is heatedup to expand to achieve the flow restrained effect, and the inlet ofcapillary gap can stop bubbles of super heat from entering, and suppressthe amount of liquid refrigerant to pass through. Therefore, a limitedquantity of refrigerant can be sucked into the compressor at a lowpressure without having the lubricating oil to return cooled. Thepresent invention eliminates the use of the evaporator or flowrestrained device, such that the compressor is the only heat generatedevice in the air heating unit of the air-conditioning. In addition, theair heating unit of the air-conditioning does not have evaporator, sothat its indoor application is not limited by weathers, even in a severecold weather outdoor. Obviously, this air heating unit of the presentinvention is one of the innovative greatest designs of this sort.

What is claimed is:
 1. An air heating unit of the air-conditioning,comprising: a compressor, with a discharge end coupled to a first linktube line provided for a high-pressure high-temperature gaseousrefrigerant and an oil to flow; a thermal compensation device, having aninner tube, a mid tube and an outer tube of different diameters, saidmid tube being sheathed with said outer tube therein, and said innertube being sheathed with said mid tube therein to form a tri-tubingstructure, and an output end of said first link tube line being coupledto said inner and outer tubes, for facilitating said high-pressurehigh-temperature gaseous refrigerant to flow and enter into said innerand outer tubes respectively, and an output end of said inner and outertubes being coupled to a second link tube line for said high-pressurehigh-temperature gaseous refrigerant and said oil to flow; an air cooledcondenser, including an internal condenser coil installed in seriestherein and having an bottom inlet end coupled to an output end of saidsecond link tube line, and a fan installed outside said air cooledcondenser, such that said high-pressure high-temperature gaseousrefrigerant charged into said condenser coil is cooled to change itsstate to form a high-pressure intermediate-temperature liquidrefrigerant containing bubbles of super heat, and said condensed liquidrefrigerant and oil flow out from the output end of said condenser coiland flow and enter into a third link tube line, and said third link tubeline having a thermostat sensor attached thereon for measuring anddetecting whether said liquid refrigerant passing through said thirdlink tube line reaches a predetermined limitation of temperature tocontrol said fan to be turned on or off, and said fan is operatedintermittently to blow air to said condenser for heating purpose; andsaid mid tube, having an intake end and an output end coupled to saidthird link tube line and a fourth link tube line respectively, such thatsaid intermediate-temperature liquid refrigerant flowing and passingsaid mid tube performs a heat transfer with said high-temperaturegaseous refrigerant flowing in said inner tube and said outer tube, andsaid intermediate-temperature liquid refrigerant is expanded by heatgain, and said bubbles of super heat of said intermediate-temperatureliquid refrigerant are blocked outside the inlet end of capillary gapbetween said mid tube and said inner tube; if saidintermediate-temperature liquid refrigerant and oil containing no airbubbles flowing out from an outlet end of capillary gap between said midtube and said inner tube flows and enters into said fourth link tubeline, the pressure is depressed at once and the temperature is loweredto form a low-pressure intermediate-temperature unsaturated liquidrefrigerant; and an output end of said fourth link tube line beingcoupled to a liquid-gas separator to disperse said low-pressureintermediate-temperature unsaturated liquid refrigerant and depress thepressure and lower the temperature again to form a low-pressure withsuitable temperature liquid refrigerant, said low-pressure with suitabletemperature liquid refrigerant and oil are sucked from a suction end ofsaid compressor to define a refrigeration cycle.
 2. The air heating unitof the air-conditioning according to claim 1, wherein said inner tube,said mid tube and said outer tube are made of copper and have differentdiameters such as ⅜″, ½″ and ¾″ inches respectively.
 3. The air heatingunit of the air-conditioning according to claim 1, wherein said firstlink tube line has a discharge end coupled to said inner and outer tubesthrough a shunt tube for facilitating said high-pressurehigh-temperature gaseous refrigerant and said oil to be delivered bysaid shunt tube to flow and enter into said inner tube and said outertube respectively, and said second link tube line has an intake endcoupled to said inner and outer tubes through a manifold tube forfacilitating said high-pressure high-temperature gaseous refrigerant tobe connected into said second link tube line.
 4. The air heating unit ofthe air-conditioning according to claim 1, wherein said condenser coilis connected in series, and said second link tube line is coupled to theintake end of said condenser coil at the bottom of said condenser, andsaid third link tube line is coupled to the output end of said condensercoil at the top of said condenser.
 5. The air heating unit of theair-conditioning according to claim 1, wherein said predeterminedlimitation of temperature is 75 Celsius degree.
 6. The air heating unitof the air-conditioning according to claim 1, wherein said fourth linktube line has a diameter greater than said outlet of capillary gapbetween said mid tube and said inner tube, and said liquid-gas separatorhas an internal diameter greater than the diameter of said fourth linktube line.
 7. The air heating unit of the air-conditioning according toclaim 1, wherein said condenser coil is surrounded by a plurality offins.